US1571577A - Compensator - Google Patents

Description

Feb. 2 1926. 1,571,57 7

J. M. DAYTON 61H07 new Feb. 2, 1926.

J. M. DAYTON COMPENSATOR AFiled August 18 1925 2 Sheets-Sheet 2 Patented Feb. 2, 1926.

UNITED STATES PATENT OFFICE.

JAMES M. DAYTON, OF HARTFORD, CONNECTICUT, ASSIGNOR TO THE DAYTON MANU- FACTURING COMPANY, OF TORRINGTON, CONNECTICUT, A CORPORATION OF CON- NECTICUT.

COMPENSATOR.

Application filed August 18, 1925.

To 1M whom t may concern:

Be it known that I, JAMns'M. DAYTON, a citizen of the United States, residing at Hartford, in thc county of Hartford, State of Connecticut, have invented certain new and useful Improvements in Con'ipensators, of which the following is a description, reference being had to the accompanying drawing and to the figures of reference marked thereon.

This invention relates to improvements 1n mechanical movements for converting an angular displacement of one element into a different angular displacement of another r element journalled coaxially with the first,

and is particularly applicable to the counting train of gasoline dispensing apparatus.

Heretofore, when counters were applied to pumps, it has been found difficult to obtain an accurate registration of the number of gallons delivered by the pump. The pump cylinders have been made of drawn tubing, and were never of an exact diameter. The amount delivered by the pump could be regulated by an adjustable stop which limited the movement of the piston, so that the volume discharged was constant from all pumps. Since, however, the movement of the piston determined the rotation of the counter, obviously with a greater cylinder diameter and a correspondingly shorter stroke, the registration was less. It has been proposed to so dispose the counter that it is only acted upon at intervals, and thus f by regulation of the intervals obtain a registration in steps: this system is subject to the disadvantage that a dishonest employee can work kthe pump between the stops defining the intervals to obtain a flow of gasoline which is not registered on the counter. n

The present invention proposes a mechanical movement to be connected between the crank handle of the pump and the counter, by which the two are at all times positively connected so long as gasoline is being drawn. The variation in length of strokes between different calibrated pumps is taken care of by a variation in the distance traveled between different parts of the driving mechanism, and particularly between two coaxiallv journalled elements.

While the invention will be described and illustrated as applied to al gasoline dispens- Serial No. 50,974.

ing pump, it will be understood.`y that it may be applied to any structure where it is.

desired to obtain a constant distance of rota'- tion from a movement of constant but arbiof the elements of the pump, compensator`- and counter.

Figs. 3, 4 and 5 are diagrams of the relative positions of the gears and pinion of the compensator.

The driving mechanism is contained within a framework consisting of the plates 10, 11. and the spacing posts 12, 13. The shaft 14 is driven by any appropriate means from the crank shaft of the pump, so that the rotation of shaft 14 is positive and at all times follows the movements of the pump piston. Mounted on the shaft 14 within the framework is a pinion 15 which meshes with a large gearwheel 16 which is loosely mounted on a stud 17 fixed to the framework.

An arm 18 is likewise mounted on the stud 17 for free movement with regard thereto, and is riveted at 19 to the gear 16 so as to partake in the movements of the latter, and move therewith through the same angle about the axis of the stud 17. The outer end of this arm 18 has an aperture to receive the reduced portion 20 of a pinion 2 1; a holding washer 22 and a cotter pin 23 hold the pinion in position in regard to the arm 18.

A compensated gear 24 preferably of the same diameter and number of teeth as the gear 16 is mounted on the end of the stud 17, which has an enlarged head 25 to prevent the separation of the various elements thereon. This gear meshes with the pinion 21 and with a driven gear 26 which is connected by a shaft 27 with one side of a ball clutch 28. rlhis clutchmay be constructed in any manner, and since a peculiar construction thereof is no part of my present invention, vit is. sufficient to state that itsv function' is to positively couple the crank handle motion with the counter 39 duringthe operation of pumping out gasoline, and to release such coupling during travel of the handle in the opposite direction, when. the pump is sucking gasoline for the next delivery. In this way the counter 89 is always driven in a single direction, and adds up the successive movements in such direction, no matter how small.

The compensating device is to provide a possible variation in the angular displacements of the positively coupled gears 16 and 24. It the pinion 21 were locked with regard to the gear 16, the gear 24 would be' driven at the identical speed of the latter. To obtain a compensation between the movements of the shafts 14 and 27 which will take care of the diiferences in piston strokes, it is necessary that the gear 21 advance the gear 24 either faster or slower than the gear 16, as the case may be.

For this purpose a sliding carriage 2S) is mounted in a slotted guideway 30 on the frame plate 11. A screw 31 with head 31a is rotatably journalled in an ear 32 fastened to this plate 11, and engages in this carriage 29, so that by rotation of the screw 31, the carriage may be moved closer to or farther from the axis of the stud 17. The carriage supports therein an arm by an end 33a serving as a pivot about an axis parallel to that ot the stud 17, but having its longer portion 33 bent at right angles and passed through an aperture` formed 1n the pinion 21 for sliding movement therein.

Vhile the various parts may be given any desired sizes appropriate to the purpose for which employed, it is preferred for gasoline dispensing devices in which seven turns of the pump handle 40 rotates the gear 15 for a full revolution to give the gear 15 twelve teeth, gear 16 forty-eight teeth, gear 24 forty-eight teeth, pinions 26 and 21 twelve teeth each. Under such conditions, a normal pump cylinder 41 which requires exactly seven turns of the pump handle to deliver ten gallons of gasoline, will cause a full revolution of gear 15 during this delivery, and therewith a,y rotation of gear 16 through 90 degrees: this should be transmitted to pinion 26 as a full revolution, which through the ball clutch 28 drives the counter for a full revolution and registers ten upon the tot-alizing wheels of the latter. Obviously to obtain an exact revolution ot the pinion 26, the gear 24 must rotate by twelve teeth or 90. In this case, therefore, the two gears 16 and 24 turn together: Which'condition is obtained if pinion 22 has no relative rotation but is merely translated by the arm 18. For this purpose the pivot point of arm 33 must coincide with the axis of the stud shaft 17, and is adjusted to such position by the screw 31.

l For a second case, however, assume that the device is applied to a pump `vvhose cylinder diameter is such that eight turns of the pump handle are necessary to deliver ten gallons of gasoline. This will cause a rotation of gear 15 through more than one revolution, and will rotate gear 16 through, say, 103 degrees. Since pinion 26 and gear 24 mesh together, and must only turn through the same angle as before (90 degrees for gear 24) to register the ten gallons delivered; it is necessary that the 103 dogree displacement of gear 16 should cause a 90 degree displacement of gear 24. For this purpose, the ypivot point of arm 33 must be displaced so that the pinion 21 will revolve sufficiently during its translation by arm 18 about the axis ot shaft 17 to reduce the total rotation of gear 24 to exactly 90 degrees. This may be accomplished by rotation of the adjusting screw 31.

Mathematically, the gear 15 will be rotated, say, through 13% tooth divisions: and gear 16 through the same peripheral distance. Since however gear 24 must onlv rotate through 90 degrees or 12 tooth divisions, it is clear that pinion 21 must lose 13?- minus 12 or 11; tooth divisions, which on a twelve tooth pinion is t ot a circumference or about 51 degrees, as represented by the angle between lines a and a in Fig. 5. This angle is derived according to Figs. 3, 4 and 5, as follows: In Fig. 3, which may be designated the initial position of the parts, it the pump handle 40 he turned to deliver gasoline or other liquid, the pinion 21 is carried upon the arm 18 counterclockwise about the axis 17. It the line joining the centers of the pinion 21 and ot pivoting portion 38" ot the arm 33 be designated ain all figures, and the line joining` the axes of the pinion 2l and the gears 16, 24 be designated as a," in Fig. 3: then as the pinion is carried counterclockwise around the axis 17, the pinion is caused to rock, with first a shortening and then a lengthening of the distance between the centers of arm 33 and pinion 21 in the example illustrated, so that the gear 24 has a lesser rotation than the armi 18. During this rocking of the pinion 21 upon the gear 24, the line of centers a in Fig. 3, becomes coincident with line a in Fig. 4, and passes to become line a in Fig. 5. As shown this angle between lines a and a. is about 51 degrees, but obviously may he made greater or 'smaller by changing the distance between the centers of arm 33 and the axis 17. During this rocking of the pinion 21 with regard to the gear 24, the latter is thus given a retrograde movement with respect to the gear 16 (or a lesser rotation with regard to the frame) of 1? tooth divisions, which just corrects the system.

The method preferably employed for adjustment of the mechanism is as follows: The pump 41 is calibrated and adjusted until it delivers exactly ten gallons. This may be done in any suitable manner, such as regulation of the lengthwise movement of the rack R by means of the adjusting screw S while pumping a liquid, until the. delivery is the required amount: this screw S is mounted on some part of the frame F, and has a lock nut L to preserve its adjustment when made.l The counting mechanism is attached, and the pump handle turned as though pumping ten gallons. The gear 16 will in this manner be turned through some angle near 90 degrees. The screw 31 is then rotated until the gear 24 lies exactly 90 degi'ees away from its original position. Since 90 degrees of movement of gear 24 represents one revolution of the counter shaft, the apparatus is now adjusted to the particular pump, and is locked at this adjustment.

It is apparent that movements of the, pump handle less than that required t0 deliver ten gallons will produce corresponding revolutions of gears 15 and 16 and of arm 18. The compensation by pinion 21 and arm 33 will be substantially correct for any fi'actional delivery. These small fractions will be added by means of the ball clutch, no matter how minute they may be.

Obvious modifications in the sizes and relations of the several parts may be made to adapt them to their employment within the scope of the appended claims.

I claim:

1. In a liquid dispensing device, a pump having an arbitrary length of stroke for a given volume of delivery, an arm, means to rock said arm through an angle proportionate to the length of stroke of said pump, a pinion carried by said arm, a gear driven by said pinion and mounted co-axially with the fulcrum of said arm, means to impose upon said pinion a movement of revolution during its translation about said gear, said gear receiving a rotation in proportion to said revolution and translation, and means to sum up the movements of said gear in one direction.

2. In a gasoline dispensing device, a pump having an arbitrary`length of stroke for a given volume of delivery, a frame, a pair of gears mounted for loose coaxial rotation in said frame, means to positively drive one gear in proportion to the movement of said pump, a pinion carried by said dr1ven gear and in mesh with the second gear, means to impose upon said pinion a movement during the rotation of said driven gear, said movement and said rotation determining the angle of rotation of said second gear, a counter driven from said second gear during the movement of the latter in one direction, and means to release said counter from said second gear during the rotation of the latter in the reverse direction.

3. In a compensating device for transmitting as uniform actuations of 'a counter the dierentlarbitrary length of stroke of any one of a number of liquid dispensing pumps which deliver calibrated equal volumes during such individual Varbitrary length of stroke, a frame, an arm pivoted on said frame, means to rock said arm from one of said pumps and in proportion to its length of stroke, a rod fulcrumed on said frame, means whereby said aim Will rock said rod about its fulcriim, means slidably carried by said rod to actuate said counter, and means to shift the fulcriim 0f said rod to attain a uniform actuation of said counter for a given volume of delivery when said device is applied to any of said pumps,

4. In a compensating devicel for transmittingas uniform actuations of a counter the diti'erent arbitrary length of stroke of any oiie of a number of liquid dispensing pumps which deliver calibrated equal volumes during such individual arbitrary length of stroke, a fulcrumed arm, means actuated from one of said pumps and in accordance with the movement thereof to rock said arm, a pinion carried by said arm, a driven gear meshing with said pinion, a rod sliding in said pinion and having a rocking movement `about a relatively fixed pivot, and means to vary the position of said pivot relative to the fulcrum of the arm to establish the coinpensation for the pump to which the device is attached.

5. In a compensating device for transmitting as uniform actuations of a counter the different arbitrary length of stroke of any one of a number of liquid dispensing pumps Which deliver calibrated equal volumes during such individual arbitrary length of stroke, a first and second member mounted eoaxially With regard to each other, a pinion carried by one of said members and in mesh with the other, a pivot, a rod mounted on said pivot and sliding in a transverse aperture of said pinion and fixing an invariable radial directive relation of said aperture and saidl pivot, and means to move said pivot relative to the common axis of said members, whereby said pinion causes a relative difference of angular movement between said members dependent upon its relative revolution as determined by said rod.

6. In a compensating device for transmitting as uniform actuations of a counter thc different arbitrary lengths of stroke of any one of a number of liquid dispensing pumps which deliver calibrated equal volumes during such individual arbitrary length of stroke, a frame, a first member pivoted on said frame, a mechanism actuated from said pump to move said first member in accordance with the length of stroke of said pump, a second member pivoted on said frame, means to connect said second member to said counter to actuate the same, a lever pivoted on said frame, a transmitting element driven by said first member and drivingsaid second member and during the transmitting movement sliding upon said lever, and means to adjust the pivot point of said lever.

7. In a liquid dispensing device, a pump having an arbitrary length of stroke for a given volume of delivery, a frame, a driver gear, means to rotate said driver gear in accordance With the movement of said pump, aV driven gear in mesh with said driver gear, an arm mounted coaxially with and driven positively bv said driven gear, a compensated gear loosely mounted coaxially with said driven gear` a pinion carried by said arm in mesh with said compensated gear, a compensator rod slidably mounted in a transverse aperture of said pinion. a relatively stationary pivot for said compensator rod attached to the frame, means to adjust said pivot linearly relative to the axis of said driven gear and to and from the axis of said, pinion, a second driven gear in mesn with said compensated gear and driven therefrom, a counter, a clutch, and means to connect said second driven gear, said counter and said clutch whereby said second driven gear drives said counter through said clutch in one direction, and rotates freely thereof in the opposite direction.

8. The combination of a counting mechanism for a pump, a continuously oscillating lever actuated with the pump, a second oscillating lever in operative relation tvith the counting mechanlsm, a fixed fulcrum for said second lever in fixed relation thereto, said second lever being actuated directly by said first lever, and means to adjust said fixed fulcrum and said second lever.

9. The combination of a counting mechanism for a pump. a continuously oscillating lever actuated with the pump, a second oseillating lever in operative relation With the counting mechanism, a fixed fulcrum for said second lever in fixed relation there to, and mechanism whereby said irst lever oscillates said second. lever at continuously varying distances from said fulcrum, and means to adjust said fixed fulcrum and said second lever.

10. The combination of a counting mechanism for a pump, a frame, a continuously oscillating lever actuated with the pump, a pivot for said first lever mounted on said frame, a second oscillating lever in operative relation with the counting mechanism, a fulcrum on said frame for said second lever, said second lever being actuated directly by said first lever, and means to adjust. the position of said fulcrum with regard to said pivot.

In testimony whereof, I aiiix my signature. i

JAMES M. DAYTON,

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